CN1161441A - Valved discharge mechanism of fluid displacement apparatus - Google Patents

Abstract

A fluid displacement apparatus comprises a valve plate member dividing a compressor housing into a first chamber and a discharge chamber. A passage is formed in the valve plate member to allow communication between the first chamber and the discharge chamber. An elastic valve member disposed on the valve plate bends to open and close the end of the passage. The valve retainer member is secured to the valve plate together with the elastic valve member and has a curved end portion. A valve seat includes a recessed portion offset from an end surface of the valve plate. The recessed portion includes an inclined portion and a wall portion extending therefrom. The distance between the beginning of the curved portion of the valve retainer member and the securing means is greater than the distance between an edge of the recessed portion of the valve seat and the securing means. Noise and vibration caused by the striking of discharge reed valve against the valve seat and the retainer member are decreased according to this arrangement.

Description

A kind of Valved discharge mechanism of fluid displacement apparatus

The present invention relates to a kind of fluid displacement apparatus, especially relate to the Valved discharge mechanism of the refrigeration compressor that uses in a kind of automotive air-conditioning system.

The Valved discharge mechanism of refrigeration compressor is known in the art.For example, Fig. 1 has described the refrigeration compressor Valved discharge mechanism that 4,978, No. 285 patents of the U.S. are introduced.Refrigeration compressor as described in it comprises a compressor case that defines a discharge chambe, and the suction of refrigerant gas, compression and discharge stroke repeat successively therein.And this compressor has comprised the valve plate 64 of cutting apart discharge chambe and drain chamber and the bleed valve assembly that is installed on valve plate 65 end faces again.Valve plate 65 has a discharge orifice 652 that discharge chambe is communicated with drain chamber.Bleed valve assembly comprises discharge reed valve 81 and valve guard 80, and they are fastened on the end face 65a of valve plate 65 together by bolt 82.The discharge reed valve made from elastomeric material 81 is regulated the flow of refrigerant gas, and when the work of compressor stops and the end face 65a sealed engagement of valve plate 65.

Valve guard 80 is in the discharge chambe and enters the exhaust campaign of restriction discharge reed valve 81 on the direction of drain chamber by discharge orifice 652 at refrigerant gas.Discharge reed valve 81 has certain elastic modelling quantity, and the pressure in discharge chambe keeps discharge orifice 652 to close before reaching predetermined value.In this structure, bound stopper 80 when discharge reed valve 81 was opened, and impacted the end face 65a of valve plate 65 when closing.Adopt the compressor of this drain valve structure when work, to vibrate and noise owing to this impact can produce.The vibration that the end face 65a that impacts valve plate 65 by leaf valve 81 causes is harmful especially, is easy to be passed to compressor case.

The solution that designer of the present invention attempted is shown in Fig. 2, although be not prior art, this trial has illustrated the progress in this field.Here, valve plate 65 has comprised a recess 650, and its degree of depth is along with the distance apart from some B prolongs and increases, and some B is positioned on the valve plate 65, with the distance of bolt 82 be L.Recess 650 has curved surface 651 around discharge orifice 652 places.When discharge reed valve 81 during in its closed position, with curved surface 651 fluid-tight engagement.Curved surface 651 has radius of curvature R 1, and it limits the distortion of closing of discharge reed valve 81.

In addition, stop 80 has the curved surface 80a that radius of curvature is R2, the distortion when its qualification discharge reed valve 81 is opened.Radius of curvature R 1 is designed to be equal to or less than radius of curvature R 2, and therefore when leaf valve 81 cut out, its elastic restoring force can not cause impacting the end face 65a of valve plate 65.The curved surface 80a of stop 80 is from 65 A beginnings of valve plate, and some A also is L to the distance of bolt 82.

In this structure, the impulsive force of the curved surface 651 of 81 pairs of valve plates 65 of discharge reed valve is less than the impulsive force to stop 80.This is because in the structure of Fig. 2, and it mainly is owing to the pressure differential between compression and drain chamber that discharge reed valve 81 is returned its closed position, rather than the elastic restoring force of discharging reed 81.Therefore, the noise that impact produced of discharge reed valve 81 is compared with the structure of Fig. 1 with vibration and is reduced.But, discharge reed valve 81 produced when this structure was not considered discharge reed valve 81 bound stoppers 80 noise and vibration.

As a result, vibration and noise still propagate into the passenger place.

An object of the present invention is to provide a kind of fluid displacement apparatus that is used for automotive air-conditioning system, this device has a Valved discharge mechanism, can reduce the vibrating noise that bleed valve assembly sends effectively, reduces to propagate into the noise at car occupant place.

Further aim of the present invention is the fluid displacement apparatus that is improved according to a kind of volumetric efficiency.

According to the present invention, fluid displacement apparatus comprises that one is divided into the valve plate of a Room and two Room with fluid displacement apparatus, and wherein two Room comprise a drain chamber.Passage runs through valve plate and two Room are discharged in one Room is communicated with.Disposed a feather valve on the valve plate, this valve is used for pressure in a Room and stops up this passage before reaching predetermined value.Stop and feather valve are fixed on the valve plate by a securing member.Valve guard has a sweep that forms in longitudinal end, is used for limiting the bending that feather valve longshore current body flows through channel direction.Open end around passage has a valve seat, and valve seat comprises a recess from the skew of the end face of valve plate, and recess has the extended therefrom wall of a sloping portion and portion.This sloping portion guarantees feather valve because drain chamber and interchannel pressure differential closing passage mildly.The beginning of valve guard sweep locate and securing member between distance greater than the edge of valve seat recess and the distance between the securing member.

Further aim of the present invention, feature and others will be understood from the most preferred embodiment of describing in detail in conjunction with the accompanying drawings of the present invention.

Fig. 1 is the local amplification profile diagram according to the bleed valve assembly of prior art.

Fig. 2 is the local amplification profile diagram of another kind of bleed valve assembly.

Fig. 3 is the vertical sectional drawing according to swash plate type refrigeration compressor of the present invention.

Fig. 4 is the local amplification profile diagram according to first embodiment of the present invention drain valve mechanism.

Fig. 5 is the drain valve mechanism cross-sectional view along the line 5-5 of Fig. 3.

Fig. 6 is for according to a second embodiment of the present invention, and cylinder internal pressure is to the relation of time T.

Fig. 7 is according to the first embodiment of the present invention, and the size of compressor noise is to the graph of a relation of compressor rotary speed.

Fig. 8 is the local amplification profile diagram of drain valve mechanism according to a second embodiment of the present invention.

Fig. 9 is the local amplification profile diagram of the drain valve mechanism of a third embodiment in accordance with the invention.

Figure 10 is the local amplification profile diagram of the drain valve mechanism of a fourth embodiment in accordance with the invention.

Fig. 3 shows according to a fluid displacement apparatus of the present invention.This fluid means is described according to piston-type compressor, but the technical staff of this professional domain will readily appreciate that the present invention goes for other fluid displacement apparatus.

Compressor has cylindrical housing assembly 20, comprises cylinder body 21, crankcase 22, front end-plate 23, end plate 24 and valve plate 25.Crankcase 22 is formed between cylinder body 21 and the front end-plate 23.Some bolt 241 (not shown) of front end-plate 23 usefulness are installed in an end (left side among Fig. 1) of cylinder body 21.Some bolt (not shown) of end plate 24 usefulness are installed in the other end of cylinder body 21.Valve plate 25 is between end plate 24 and cylinder body 21.Opening 231 is shaped at the center of front end-plate 23, and by bearing 30 supporting driving shafts 26, the inner of driving shaft 26 is supported by bearing 31 rotations that are configured in cylinder body 21 central bore.Endoporus 210 extends to the rear end face of cylinder body 21, and the there disposes a valve control device 212.

Cam follower 40 usefulness pivot pins 261 are fixed on the driving shaft 26, together rotate with driving shaft 26, and thrust needle bearing 32 is configured between the axial end of the inner face of front end-plate 23 and contiguous cam follower 40.Cam follower 40 has arm 41, and pivot pin 42 extends out from it.Swash plate 50 and cam follower 40 adjacency have opening 53 on it, driving shaft 26 therefrom passes.Swash plate 50 comprises the arm 51 that fluting 52 is arranged on it.Cam follower 40 is connected with pin 42 with swash plate 50.Fluting 52 allows to adjust the angle position of swash plate 50 with respect to driving shaft 26 longitudinal axis.

Oscillating deck 60 by bearing 61 and 62 nutatings be installed on the swash plate 50.Fork-shaped slide block 63 is slidably mounted on around the slide rail 64 attached to the outer end of oscillating deck 60, and slide rail 64 is sandwiched between front end-plate 23 and the cylinder body 21.Fork-shaped slide block 63 stops oscillating deck 60 to rotate when cam follower 40 rotates, and makes oscillating deck 60 along slide rail 64 nutatings.Some cylinder chamber 70 along circumference are arranged in the cylinder body 21, and piston 72 is reciprocating in cylinder chamber.Each piston 72 links to each other with oscillating deck 60 with respective link 73.

End plate 24 upper edge circumference ring-type absorption chambers 142, and the center is a drain chamber 152.Valve plate 25 has some valve suckings 242 to be connected with each absorption chamber 142 with respect to cylinder chamber 70 between cylinder body 21 and end plate 24 on it.Also there are some valve discharge orifices 252 that drain chamber 152 is linked to each other with cylinder chamber 70 on the valve plate 25.

Each absorption chamber 142 has a suction inlet to link to each other with an evaporimeter (not shown) of external refrigeration circuit.Drain chamber 152 provides notch portion and links to each other with the condenser (not shown) of cooling circuit.The mating surface of pad 27 and 28 sealed cylinder blocks 21, valve plate 25 and end plate 24.

Dish is adjusted screw 33 devices in the inner end portion of driving shaft 26 and endoporus 210 centres between the valve control device 212.Dish adjustment screw 33 screw-in endoporus 210 make it pass through packing ring 214 and contact with the inner face of driving shaft 26, and can adjust the axial location of driving shaft 26.Piston component 71 comprises connecting rod 73, and its two ends form spherical part 73a and 73b and are connected to the cylindrical piston 72 of ball portion 73b.

With reference to figure 4 and Fig. 5, bleed valve assembly comprises discharge reed valve 81 and valve guard 180, and they are fixed on the valve plate 25 with bolt 82.The drain valve leaf valve of making as thin spring steel with elastomeric material 81 is regulated the flow of refrigerant gas.Discharge reed valve 81 has one at the basic flat part 81a of bolt 82 1 sides formation with from the extended hermetic unit 81b of 81a part.

Valve plate 25 comprises recess 250, and its degree of depth strengthens along with the radial distance from a C and increases, and some C is L1 apart from the length of bolt 82.Recess 250 has the curved surface 251 around discharge orifice 252.When discharge reed valve 81 during in its closed position, sealed engagement inclined plane or curved surface 251, curved surface 251 begins to have curved cross-section and radius of curvature R 3 from a C.When discharge reed valve 81 was vibrated as fulcrum with fixing point C shown in cutaway view, curved cross-section limited the peak swing of intrinsic vibration.In other words, the intrinsic vibration shape approximation of discharge reed valve 81 is that radius of curvature is the curve of R3.

Recess 250 has 251 end walls that extend out 254 from the inclined-plane.When discharge reed valve 81 sealing inclined-planes 251, sidewall 254 is preferably parallel with the outer rim 81c of leaf valve 81.Between the edge 81c of the end wall 254 of valve plate 25 and discharge reed valve 81, produce a gap.On the valve 25 at discharge orifice 252.Other parts recess 250 and there, as, the front end 253 common sealings that constitute valve on inclined-plane 251, end face 25a and inclined-plane 251.

And valve guard 180 comprises two surface portions, and planar section 180a and curvature portion 180b are that the some D at L2 place is the boundary with the length of distance bolt 82.From a D beginning, curved surface 180b has the cross-section curves that radius of curvature is R4.When discharge reed valve was the fulcrum vibration with a D, cross-section curves limited the peak swing of intrinsic vibration.In other words, the intrinsic vibration shape approximation of discharge reed valve 81 is the curve of R4 in radius of curvature.In addition, valve guard 180 the most handy resins or engineering plastics are made, as poly-diethanol resin.

Valve guard 180 is at the bending motion of refrigerant gas by restriction discharge reed valve 81 on the direction of discharge orifice 252, the bending of discharging reed 81 along with its opening and closing discharge orifice 252, and have certain elastic constant so that the pressure of leaf valve 81 in discharge chambe 70 stops up discharge orifice 252 before reaching predetermined value.Pass between L, L1 and the L2 is L1＜L＜L2

At the fluid displacement apparatus duration of work, driving shaft 26 passes through electromagnetic clutch 300 driven rotary by vehicle motor.Cam follower 40 is driven by driving shaft 26, and driving shaft 26 also rotates swash plate 50, and swash plate 50 makes oscillating deck 60 nutatings successively.The nutation movement of oscillating deck 60 makes piston reciprocating in their cylinders 70 separately.Along with the reciprocating motion of piston 72, refrigerant gas is inhaled into absorption chamber 142 by intake section, is compressed then.Compressed refrigerant gas is discharged into drain chamber 152 from each cylinder 70 through discharge orifice 252, enters the cooling circuit by exit portion therefrom.

The impulsive force of 81 pairs of stops 180 of discharge reed valve less than in the structure of Fig. 1 and Fig. 2 to the impulsive force of stop 80.This is because realized the bending of easier prevention discharge reed valve 81 to stop 180 in the situation of Fig. 4, and discharge reed valve 81 is easier in stop 80 bendings in the structure of Fig. 1 and Fig. 2.Make the size of bending rigidity of the discharge reed valve 81 of leaf spring shape, distance general and to fulcrum is inversely proportional to.Distance L 2 among Fig. 4 is greater than the distance L among Fig. 2.Bending rigidity when discharge reed valve 81 its bending rigidity that is fulcrum with fixing point D when stop 180 is crooked is fulcrum with an A in less than Fig. 2 (or Fig. 1).As a result, noise and vibration that discharge reed valve 81 bound stoppers 180 produce are got back to its inclined-plane 251 rapidly in the beginning of absorption stage.This improvement makes discharge reed valve close discharge orifice reliably in expiratory phase.

Fig. 8 illustrates second most preferred embodiment of the present invention.Among Fig. 8 with Fig. 4 in similar element give identical label.Valve plate 25 has recess 250, and its degree of depth is along with elongating with the distance of a C and increasing, and some C is positioned on the valve plate 25, and the distance of 82 of set bolts is L1.Recess 250 has the curved surface 351 around discharge orifice 252, and when discharge reed valve 81 during in its closed position, it contacts with curved surface 351 sealings.

Inclined-plane 351 has a cross-section curves of being made up of four curved sections, and the radius of curvature of four curved sections is respectively the R7 of R3, R5, R6.First curved section begins till the E from a C.Straight line M parallel with the end face 25a of valve plate 25 and by the some C.First curved section and straight line N intersect, a straight line N and mistake point E parallel with straight line M.Second curved section begins to terminate in a F from an E.Second curved section also intersects with straight line p, a straight line P and mistake point F parallel with straight line M.The 3rd curved section begins to terminate in a G from a F.The 3rd curved section also intersects with straight line Q, a straight line Q and mistake point G parallel with straight line M.The 4th curved section begins to terminate in a H from a G.The 4th curved section also intersects with straight line S, a straight line S and mistake point H parallel with straight line M.Straight line N, P and Q are divided into quarter to the distance between straight line M and each straight line.Radius of curvature R 3 is similar to the intrinsic vibration shape of discharge reed valve 81.Pass between R3, R5, R6 and the R7 is R7＜R6＜R5＜R3

In the analysing and observe as shown in Figure 8, be fulcrum when doing intrinsic vibration with a C between the curve shape of cross-section curves and leaf valve 81, the peak swing place produces small air gap.In this structure, realized the identical advantage of the first best enforcement in fact.In addition, the impulsive force on 81 pairs of inclined-planes 351 of discharging reed is less than the impulsive force of Fig. 4 structure.This is that it is less than the radius of curvature on inclined-plane among Fig. 4 251 because the inclined-plane 351 among Fig. 8 has the radius of curvature of variation.

Fig. 9 illustrates the 3rd most preferred embodiment of the present invention.Among Fig. 9 with Fig. 4 in similar element give identical label.

Plane 451 has the line transversal face that begins to terminate in a H from a C, rather than cross-section curves.Shown in cutaway view, be fulcrum during with a C between the curve shape of line transversal face and leaf valve 81 with natural frequency vibration, that supposes produces small air gap at its peak swing place.Realized the advantage identical in fact with first most preferred embodiment.

Figure 10 illustrates the 4th most preferred embodiment of the present invention.Among Figure 10 with Fig. 8 in similar element give identical label.Recess 250 has the curved surface 551 around discharge orifice 252, when discharge reed valve 81 during in its closed position, contacts with curved surface 551 sealings.

Inclined-plane 551 has a cross-section curves of being made up of four curved sections, and the radius of curvature of four curved sections is respectively R3, R8, R9 and R10.Pass between R3, R8, R9 and the R10 is R3＜R8＜R9＜R10.

Shown in Figure 10 be fulcrum when doing intrinsic vibration between the curve shape of cross-section curves and leaf valve 81 in analysing and observe with a C, produce small air gap at the peak swing place.In this structure, realized the advantage identical in fact with second most preferred embodiment.

Fig. 6 and 7 illustrates the relation between the device of the device of most preferred embodiment and Fig. 2.Fig. 6 depicts the relation of inner cylinder pressure to time T.Demonstrate most preferred embodiment and reduced the time-delay that discharging reed 81 cuts out, in addition, Fig. 7 illustrates the relation of the size of the noise that compressor causes to compressor rotary speed.Compare with the noise that the compressor of Fig. 2 produces, most preferred embodiment has reduced the noise level of compressor.

Although the present invention is described in conjunction with most preferred embodiment, be not limited to this.Those of ordinary skill in this professional domain understanding easily is easy to change and revise in the scope of the invention that claim limited.Like this, by the fluid displacement apparatus of most preferred embodiment with particular type, swash plate type compressor for example, the present invention of expression can be applied in the fluid displacement apparatus of any other type, as the volute type displacement apparatus.

Claims (10)

1, a kind of fluid displacement apparatus, by constituting with the lower part:

A shell that comprises front end-plate and end plate;

A valve plate that is assemblied in the described shell is divided into first Room and second Room to described shell, and described second Room comprises a drain chamber.

A passage that between described first Room and described drain chamber, on described valve plate, forms, described passage has an openend, and fluid discharged flows by it;

A feather valve that is assemblied on the described valve plate, described valve have an elastic constant makes the pressure of described passage in described first Room keep closing before reaching predetermined value;

Valve guard on the described valve plate that fastener is fixed on, described valve guard is to the direction bending of leaving described valve plate, and described valve guard limits the bending motion of described valve; With

A valve seat that on described valve plate, forms around the openend of described passage, described valve seat comprises a recess that forms on described valve plate, described recess comprises an inclined-plane that increases gradually along described valve plate radial depth, described inclined-plane is more radially outer from described securing member, and described valve guard is radially outward crooked from this.

2, the described fluid means changing device of a claim 1, the described inclined-plane of wherein said recess comprises a curved section, described cross-section curves has a radius of curvature at least.

3, the described fluid means changing device of claim 2, described at least one radius of curvature of wherein said cross-section curves is approximately the peak swing of described elasticity intrinsic vibration.

4, the described fluid means changing device of claim 1, the described inclined-plane of wherein said recess comprises the cross-section curves that some curves of a radius of curvature with variation constitute, and described radius of curvature increases along with the radial distance with described securing member and reduces gradually.

5, the described fluid means changing device of claim 1, the described inclined-plane of wherein said recess comprises the cross-section curves that some curves of a radius of curvature with variation constitute, and described radius of curvature is along with the radial distance with described securing member increases and increases gradually.

6, the described fluid means changing device of claim 1, the described inclined-plane of wherein said recess has a line transversal face.

7, the described fluid means changing device of claim 1 produces an air gap when described feather valve reaches the peak swing of its intrinsic vibration between the described inclined-plane of described recess and described feather valve.

8, the described fluid means changing device of claim 1, the described curved surface of wherein said stop has a cross-section curves that has a radius of curvature at least.

9, the described fluid means changing device of claim 8, wherein said at least one radius of curvature is approximately the peak swing of described feather valve intrinsic vibration.

10, the described fluid means changing device of claim 1, wherein said stop is made by engineering plastics.

Images